Gear-cutting machine



Jul 6, 1948. o. F. BAUER 2,444,551

GEAR CUTTING MACHINE 7 Sheets-Sheet 1 Filed Nov. 9, 1944 Zhwentor OLIVER F. BAUE Gttorucg July 6, 1948. o. F. BAUER 2,444,551

GEAR CUTTING MACHINE Filed Nov. 9, 1944 7 Sheets-Sheet 2 Zhwentor OLIVER f1 BAUER,

l i Gttomeg July 6,1948. o, F, A ER 2,444,551

GEAR CUTTING MACHINE Filed Nov. 9, 1944 '7 Sheets-Sheet 3 Sunentor OLIVER, i; BAUER July 6, 1948. o. F. BAUER I I 2,444,551

GEAR CUTTING MACHINE Filed Nov. 9, 1944 "7 Sheets-Sheet 4 July 6, 1948.

Filed Nov. 9, 1944 0. F. BAUER GEAR CUTTING MACHINE 7 Sheets-Sheet 5 Imventor @LIVBR, F: ,BAUER,

f i N9" Gitorneg GEAR CUTTING MACHINE Filed Nov. 9, 1944 v Sheets-Sheet e 3nnentor @LEVER BAUER,

jufiy mg. G. F. BAUER 294M551- GEAR CUTTING MACHINE Filed Nov. 9, 1944 '7 Sheets-Sheet '7 1/3 I r I Snventor Q LIVER, f: BAUER (Xttomeg Patented July 6, 1948 TATES TENT DFFI CE GEAR-CUTTING TviACHINE of New York Application November 9, 1944, Serial No. 562,608

The present invention relates to machines for producing gears and particularly to machines for generating spiral bevel gears of small size.

In the generation of spiral bevel gears, a facemill gear cutter is ordinarily used as the cutting tool, and, as the cutter rotates in engagement with the work, the cutter and the work are rolled relative to one another as though the gear, which is being cut, were rolling with a basic gear represented by the cutter. It has been proposed to cut spiral bevel gears by continuous indexing processes, but conventional spiral bevel gear cutting machines operate according to the intermittent indexing process. In a machine operating by the intermittent indexing process, the operating cycle comprises movement of the cutter and work into operative relation, roll of the rotating cutter and work together to generate a tooth side or a tooth space of the work, withdrawal of the cutter from engagement with the work, and indexing of the work.

Heretofore, small-sized spiral bevel gear gen.- erators have been of the segment-roll type, that'is. they have been so constructed that the generating roll is produced by a pair of segments, one of which is connected to the work spindle and the other of which has a fixed relation to the cutter. Either the work or the cutter may be mounted on an oscillatory cradle which is oscillated and-which, when oscillated, causes one segment to roll on the other, imparting rotation to the work spindle in time with the cradle movement. This timed rotation of the cradle and work spindle constitutes the generating roll of'the machine.

Segment-roll machines are more or less special purpose machines, because for each different job, ordinarily, at least a different work segment has to be employed. Moreover, when the machine is provided with a notched-plate type of ind-ex mechanism, different notched plates have to be used when gears of different tooth numbers are to be cut. The smaller type spiral bevel gear generators as heretofore built have, therefore, not been particularly suited to jobbing work because of the number and the cost of the segments and of the index plates required to cover the full range of the machine.

Some small spiral bevel gear generators have been built which are'of the geared-roll" type.

these machines, the gener'atingroll is effected through a train of gearing which drives the oscillatory cradle and the work spindle in the required timed relation. These machines have one advantage, so far as jobbing work is con.-

13 Claims.

cerned, namely, the ratio of roll can be varied for different jobs simply by substitution of different change gears. These machines as heretofore built, however, have also employed a notched-plate type of index mechanism.

It is ordinarily desirable to cut simultaneously both sides of each tooth space in small-sized spiral bevel gears. Where both members of the pair are cut in this manner, however, bias bearing will be encountered when the two members of the pair are run together, unless some special method of generating the gears is employed to obviate this bearing condition. One known method is disclosed in the Wildhaber Patent No. 1,980,365 of November 13, 1934. In this method in addition to the conventional motions, an added motion is effected between cutter and. work in the direction of the axis about which the generating roll is taking place. This method can. be practiced on gear-cutting machines of known construction, both of the segment-roll and of the geared-roll type, by forming the .cam, which produces movement of the work into and out of operative engagement with the tool, so that this cam will, during generation, produce the required additional movement in the direction of the axis of generation.

Because this additional movement is in the direction of the axis about which the rolling motion takes place, it is conventionally termed a helical motion." The amount of helical movement, which is required, is small compared with the amount of movement necessary to move the tool and work into and out of operative relation. It is difiicult, therefore, to design suitable cams to perform both functions. Further than this, when the helical motion is employed, a different cam is required for each difierent job.

A primary object of this invention is to provide a machine for generating small-sized spiral bevel gears which will be much more universal than any such machine heretofore built.

A further object of the invention is to provide a spiral bevel gear generating machine for smallsized Work in which the indexing mechanism, as such, may be eliminated entirely.

Another object of the invention is to provide a spiral bevel gear generating machine for cutting gears with a helical motion in which a simple and practical control mechanism is provided for governing the helical motion.

Still another object of the invention is to provide a spiral bevel gear generating machine for cutting gears with a helical motion in which a single cam may be used to efiect with this mo- 5 The swinging base I is mounted for angular adjustment on the sliding base 20. The angular adjustment of the swinging base on the sliding base is about the axis of a stud I (Figs. 1 and 6) which is secured in the sliding base 20 and on which the swinging base is pivoted. A nut 16 which threads onto this stud serves to hold the swinging base against movement axially of the stud.

During operation of the machine, the cutter C rotates continuously on its axis, the cradle I1 is oscillated back and forth about its axis, the work spindle 35 is rotated continuously on its axis, and the sliding base 20 moves, prior to each cutting operation, toward the cradle, to bring the work into operative engagement with the cutter and, after each cutting operation, is moved away from the cradle, to withdraw the work from engagement with the cutter, so that the continued rotation of the work may index the work. If helical motion is employed, the sliding base also has a movement during cutting either toward or from the cradle.

The various parts of the machine are driven from a motor 60 (Fig. 12) which may be mounted at any convenient point on the machine. The armature shaft 8| of this motor is connected through a suitable coupling 82 with a shaft 83. This shaft drives the shaft 84 through the miter gears 85 and 86. Shaft 84- drives a shaft 88 through a set of change gears 89, 90, 9|, and 92. The shaft 88 drives a shaft 94 (Figs. 12 and 1) through a pair of miter gears 95 and 96. There is a bevel pinion 91 secured to the shaft 94 and this pinion meshes with a bevel gear 98 that is secured to the rear end of the cutter spindle 26.

The oscillatory movement of the cradle I1 is produced and controlled by a rotary cam I00 (Figs. 2 and 12). This cam is so shaped as to impart motion at'a uniform rate to the cradle during generation and to return the cradle to initial position at fast speed when cutting on a tooth surface or a tooth space of the work has been completed. The cam-engages one arm of a lever ml which is pivotally mounted in the bed of the machine on a stud I02. The lever IOI is adjustably connected to a link I04. The link carries a pin I05 at one end which is rotatably mounted in a block I06 that is slidably adjustable in an elongated slot I0'I formed in the lever arm II". The link I04 is adjustably connected at its opposite end through a bolt I08 with the cradle II. The bolt I08 may engage in an arcuate slot formed in the flange I09 (Fig. 1) 0f the cradle coaxial of the cradle. This slot should be of sufficient angular extent to permit of the required adjustment of the cradle for gears of different spiral angles.

Adjustment of the block I06 and pin I05 in the slot I01 of lever IOI permits of adjusting the amount of throw of the cradle to conform to the amount of generating roll desired. This adjustment may be effected by rotation of the screw H0 which threads into the block I06 and which is journaled in the lever IOI. A graduated dial I I I, that is secured to the screw, permits of making this adjustment precisely.

The cam I00 is mounted on a flange-portion I I2 of shaft H3 so that the geometric center I03 of the cam is eccentric of the axis of shaft H3. The cam is secured to the flange H2 by a bolt H4 and dowel pins H5.

To counterbalance the cradle I1 and to hold the lever IOI against the periphery of the cam I00, a counterweight I26 is provided. This counterweight (Fig. 2) is connected to the cradle by a chain I21. The chain is guided by a sprocket wheel I28 which is rotatably mounted on a housing I28. This housing is secured in the column or upright I6 and contains the counterweight I26. A coil-spring I33, which is interposed between the upper end of the housing and the weight I26, serves to assist the counterweight in its work.

The shaft H3 is driven from the shaft 84 through change gears I I6, I", I I8, and H8 (Fig. 12), the shaft I20, bevel gears I2I and I22, the shaft I23, bevel pinion I24, and the bevel gear I25 (Figs. 12 and 1). The last named gear is keyed or otherwise fastened to the shaft H3. The shaft H3 fits into one end of a shaft I30 and is keyed to that shaft. The shaft I30 is journaled at one end in a bearing I3I that is secured to the bed of the machine and at its opposite end in a bearing I32 which is also secured to the bed of the machine (Fig. 8).

Keyed or otherwise fastened to the shaft I30 is a control member I34. This control member is formed to have two spaced slots extending around its periphery. One of these slots, the slot I35, is a cam slot and is so formed as to produce feed of the work into the tool prior to generation, dwell of the work in operative position during generation, withdrawal of the work away from the cutter at the end of a generation cycle, and dwell of the work in withdrawn position for a sufficient length of time to permit the continuous rotation of the work to index the work. The slot I36 is a simple annular slot without lead. Its purpose will appear hereinafter.

Secured to or integral with the control member I 34 is a cam member I38. The portion of the peripheral surface of this cam, which is in operation during cutting, is formed on a spiral of uniform lead coaxial with the axis of the shaft I30, thereby to produce the helical motion required for elimination of bias bearing.

Pivotally mounted on the stud I40 (Figs. 8, 9, and 10), which is secured in the bed of the machine, is a lever arm I4 I. Mounted on a stud I42, which is secured in the lever arm I4'I, is a roller I43. This roller engages in the cam path or slot I35.

Pivotally mounted on a stud I45, which is journaled in the lever arm MI, is a lever I46. Secured in the lever I is a stud I41 on which is rotatably mounted the cam roller I48. This cam roller is adapted to engage the periphery of the cam I38. The roller I48 is held in engagement with the peripheral surface of the cam I38 by a spring-pressed plunger I (Figs. 3 and 10) which is constantly urged into engagement with the lever I46 by a coil spring I56 that is housed in a tube I51 which is secured on the lever arm I4I to move therewith.

Integral with the lever I46 is a stud I49 (Fig. 8) on which is rotatably mounted the roller I50. The roller I50 engages in a slot I5I (Figs. 3, 6, and '7) which is provided in a rotatably adjustable plate I52 that is secured by screws I53 and a disc I58 to a sliding block I54. The block I54 is adjustably secured to the sliding base 20 as will be described more particularly hereinafter.

The plate I52 may be adjusted on the block I 54 by rotation of the shaft I60 (Figs. 6 and 7) which is journaled in the sliding base 20. This shaft carries a worm I6I which meshes with a worm wheel segment I62 that is cut on the periphery of the plate I52. Adjustment of the plate I52 =.:can-.lie made precisely by use pf :the graduated @di'al 1.1% which is secured -;to shaft 169.

-As will-be obvious, as "the shaft {I30 revolves, the leverirldz'i will-be rockedabout its pivot --I45 throughactionlof cam-1236., As theishaftltfl re- 'volves-ithe lever arm- I 2.1 "will: alsobe 12o cked-about its? pivot hlll through-action f %th;e 'camv path +35. When-the lever :arm zllll :is rocked about its-pivot 'I HL'the lever I46 willa1so be rockedwabout this same-pivot I Ml. Since'thelever arm-114$ carries :the roller I58 which'engagesin the slot !5I of plate I52, and 'sinceplate I52 is adjustably sezcured to block'l' l, and sinceblock I54=is "ad- 'ju'stably secured to sliding base 429, it will be obvious'that when. lever arm id! is roclred,-the sliding .base 28 will be'moved on the'bed of the machine.

The cam path -I 35-,rocksthe lever arrn- Ml prior to'cutting to'cause the work to be moved into engagement with the cutter, and after cutting, to cause the work tobe disengaged-from the cutter for indexing. If the member; I52 isinthe Zero position of its adjustmentcthat is, lithe slot -.I 5! is perpendicular to the direction-of movement .of'the sliding base 2i), as shown in Fig-6, the

..roller 1530f lever 4456 will rockidly back and forthin slot I5! under actuation of cam E38 and the only movement imparted to the sliding-base during airevolution of the shaft I35) will then be that caused by the cam path I35. If the member I52 is adjusted, however, so that the slot i5! is in- .clined-at. other than right angles to the direction of movement of the sliding base 28, as for instance if slot I5I is in the position shown in Fig. 7, then .as the shaft I39 revolves, the lever arm M8 under actuation'of camltfl will impart movement to the sliding base 20. Thismovement .will be additional to that eilected by cam path I35, and will be determined by the angular setting of plate I52. It will take place during actual cutting of a tooth space of the work, and since it is in the direction of the axis of the cradle ll, will eliminate bias bearing as described inthe Wildhaber Patent No. 1,980,365, above mentioned.

Where the helical motion is not employed, it is desirable to limitdefinitely the depth of engagement of the work with the cutter. For this purpose, a stop lug IIil (Figs. 6 and 7) is provided.

This stop lug is secured to the adjustable plate stop-lug can readily clear the stop member when the plate I52 is adjusted angularly.

The depth of the tooth spaces, which are to be cut in the gear, may be adjusted by adjustment of the block I54. Adjustment of this block may be effected by rotation of the shaft I74 which is journaled in the sliding base 29 and which threads into the block I54.

After adjustment, the block I54 is secured in adjusted position by axial adjustment of the rod I16. the sliding base and has a tapered or wedgeshaped nose I" at its inner end, asshown in Fig. 11. This tapered nose is adapted to enter a wedge-shaped slot provided in a member I18 which engages in one of the gibs I19 that serve .to secure the block I54 to the sliding base 20.

"It will be obvious that when the rod I16 is adjusted inwardly, the member I18 =will be forced upwardly to force the gib I19 upwardly and clamp the' block I 54- in anyadjusted position. Recti- This rod is mounted for axial movement in linearaadjustmentof the-rod I16 iseffectedby'rotationofithe nut-I-'I-5-which is'rotatably adjustablerin-the sliding base 20- and which is internally threaded to engage an externally threaded. portionof rod I16.

The sliding basal 28 isnot withdrawnsufficiently after-each cutting-operation by cam path I35 to permitremoval of-a completed, gear from the machine and chucking of a new work-piece. To

move the sliding-base to and from-loading position, a hand lever I (Figs. 3 and 8) is provided.

This hand lever is securedto a shaft I 85 that is journaledinrthe bed of the machine and it has anarm I81 at its innerend. A roller I88 is mounted on-the arm I81 eccentrically of the axis of the shaft I86. This roller engages in the slot I-36-of:thecontrolrmember I34. -When the lever I 85is'rocked in one direction or the other, the control member I34 is moved-bodily axially on the shaft-I30. This causes the lever arm' It! to be rocked-about pivot stud on, and thus, the sliding base is moved to or-from loading position depending upon the diIGCfiOlllIl-WhlCh the lever I85 is rocked.

The sliding base-.20 is normally urged toward ifully withdrawn or loading position by a coil spring I80 (Fig.6). This spring is mounted in a tube I8I which is secured in the bed of the mach'ine. This coil spring I89 engages the enlarged headof a rod- I82 whichis secured in the sliding base-2D. The amount of tension-on the spring I80-can-be-adjusted by adjustment of the nut 484 whi'ch'threadsinto the bed of the machine and through which the rod I82 extends.

During operation of the machine, the work is driven-continuously, the drive being from the shaft-I23 (Fig. 12) through the mitre gears I99 and ISI (Figs. land 12), the overhead telescopingshaft I92, the mitre gears I93 and I534 (Figs.

l=ar-1d l2), vthe shaft I95 which has telescoping engagement with the gear. I9 and which isjournaledcoaxially in the sleeve member I5 I, the mitre gear-I9B which is secured to the lower end of this shaft, the mitre-gear I87, which is secured to a shaft IE8 (Figs. 4,5, and 12) which is journaled inst-gear boxZIM, the change gears I 99, 200, 20I, and 202, the shaft 2Il5,'thebevel pinion 296 and the bevel gear 291. The latter is keyed to the work spindle 35 of the machine. The change gear box-2B4 has a portion which extends through an elongated opening-203-in the column 50 and which is fastened to work head 40. The change :gearsIflS, 200, 2M and 282, which govern the number-of teeth-to he cut in the work, are enclosed in-the-change gear box-2B4. These change I gears are lubricated through a line 288 (Fig. 3)

which is connected to one sidev of piston 42. The lubricant exhausting from the change gear box flows back to the sump of the machine through a duct 209.

There is a plate 2W (Figs S, 9 and 12) secured to the shaft I30 to rotate therewith. This plate has a lug 2| I- formed on its rear face, and during each revolution of the plate this lug engages a lever-U2, which is pivoted on a pin 2H3 in the bed I5, and rocks that 'lever about its pivot. This lever engages a plunger 2 I5 :01? an electrically operated counter mechanismil i. The plate 2H! revolves once for each cycle of operation of the machine. The counter mechanism is therefore tripped through the lever 2E2 once on each cycle of operation of the machine. The counter mech- .aretooth spaces in theblank tobe cut. Thus when a gear is completed, the machine is stopped.

The operation of the machine will be understood from the preceding description but may briefly be summed up here. Assuming that the required adjustments of the cutter and the work have been made to cut a gear of the desired spiral angle, cone distance and tooth depth, the operator moves the work into operative relation with the cutter by swinging the lever I85 (Fig. 3) in a counterclockwise direction, causing the control member I34 to be shifted forwardly on the shaft I30 thereby rocking the lever arm I II on its pivot I40 and moving the sliding base into operative position. When the sliding base is in operative position, the machine may be started. The cutter is then driven continuously on its axis through operation of the gearing already described, and the cam shaft I30 and work spindle 35 are also then driven continuously through the gearing already described. As the cam shaft rotates, the cam path I35 engaging the roller M3 first causes the sliding base to be fed forwardly to move the work into engagement with the cutter. Then the generating roll begins and the cradle is rocked on its axis in one direction through the operation of the cam I and link member I04 in time with the work rotation. If the adjustable member I52 (Figs. 6 and '7) is in zero position, the sliding base dwells in its forward position, determined by stop I (Fig. 6), during the generating roll. If the adjustable member I52 has been adjusted, however, out of zero position, the lever I46 slowly feeds the work at a uniform rate either into or away from the cutter as the cutter rolls in engagement with the work. At the end of the generating roll, when a tooth space of the blank has been cut, the cam I03 causes the direction of movement of the cradle to be reversed and the cam path I35 causes the sliding base to be withdrawn to disengage the work from the cutter. The work will continue to rotate, however, in the same direction during the return roll of the cradle as during cutting. This operates to index the blank. When the return roll of the cradle has been completed, the cam path I35 operates to move the sliding base forward again to bring the work again into engagement with the cutter and the cycle begins anew. The operation of the machine is continuous with feed of the work into the cutter, generation, withdrawal, and return roll for each tooth space to be cut.

0n each revolution of shaft I30, the lever 2I2 is operated to trip electrical counter 2M. When the desired number of teeth have been cut in the gear, then, the machine is stopped. The operator can then withdraw the sliding base to loading position by use of lever I85 (Fig. 8), dechuck the completed gear, and chuck a new blank,

While the invention has been described in connection with a particular embodiment thereof and in connection with the production of spiral bevel gears, it will be obvious that various features of the invention may be employed on machines for generating gears of other types and in fact may be employed on other types of machines. It is to be understood, therefore, that this application is intended to cover any adaptation or embodiment of the invention following, in general, the principles of the invention, and including such departures from the present disclosure as come within known or customary practice in the gear art and as may be applied to the essential features hereinbef'ore set forth and as fall within the scope of the invention or the limits of the appended claims.

Having thus described my invention, what I claim is:

1. In a machine for generating gears, a frame, a cradle oscillatably mounted on the frame, a work support reciprocably mounted on the frame, a face mill cutter journaled in the cradle, a work spindle j ournaled in the work support, means for rotating the cutter, means for rotating the work spindle continuously at a uniform velocity, means driven in time with the last named means for oscillating the cradle to impart thereto alternate generating and return movements, means for reciprocating the work support to move the work into and out of engagement with the cutter and so operated that the work is in engagement with the cutter during the generating movements of the cradle and is out of engagement with the cutter during the return movements of the cradle.

I 2. In a machine for generating gears, a frame, a cradle oscillatably mounted on the frame, a slide mounted on the frame for movement toward and from the cradle in the direction of the axis of the cradle, a tool support mounted on the cradle, a face mill gear cutter journaled in the tool support, a work support mounted on the slide, a work spindle journaled in the work support, means for rotating the cutter, means for rotating the work spindle continuously at a uniform velocity, means driven in time with the last named means for oscillating the cradle to impart thereto alternate generating and return movements, means for reciprocating the slide to move the work into and out of engagement with the cutter and so operative that the work is in engagement with the cutter during the generating movements of the cradle and is out of engagement with the cutter during the return movements of the cradle, and separate means for moving the slide in time with the cradle durin the generating movements of the cradle.

3. In a machine for generating gears, a frame, a cradle oscillatably mounted on the frame, a .work support reciprocably mounted on the frame, a work spindle journaled in the work support, a face mill gear cutter journaled in the cradle, means for rotating the cutter, means for rotating the work spindle continuously at a uniform velocity, means for oscillating the cradle comprising a rotary plate, a cam eccentrically mounted on the plate, a lever pivotally mounted in the frame and engaging the cam at one end, a link adjustably connected at one end to the opposite end of the lever and a-djustably connected at its opposite end to the cradle, and means for rotating the plate continuously at a uniform velocity in time with the means for rotating the work spindle.

4. In a machine for generating tapered gears, a frame, a work support, a tool support, a cradle oscillatably mounted on the frame and on which one of said supports is mounted, a slide mounted on the frame for movement in the direction of the axis of the cradle and on which the other support is mounted, a work spindle journaled in the work support, a face mill gear cutter journaled in the tool support, means for rotating the cutter, means for rotating the cradle and work spindle in timed relation to effect generation of the tooth profiles, a rotary cam journaled in the frame, a lever operatively connected to the cam, a block mounted on the slide having a diametral slot therein in which the lever engages to operatively connect the cam with the slide, said block being l ll assessable tc van'r theeneie (ir s-entrants of tlie slot to the direction of mcvernerit: ft the slide, thereby t6 Var? the amouut'ermovement cr the slide during rotation of the cam, and me'an's for' rctati gthe cam m time with the-rotary; movements of the cradle and vv'ork'- spindle;

fiil'ri e'm'eeninerer producihg tapered gears,

afia'me; were support,- a toolsupport, a cradleoscillat'ably mounted' onthe 1 frame i and on which one of s'aid supports is mounted; aslide mounted cutter, meansfor rotating the cradle and work spindle-in timedrelatioiito generate the tooth profil neve pivotal-1y mountedinthe frame, en i-iitime thegefieralting motion a said lever about i'ts pivot through a given angle;- adjustable for connecting the l'eve'r'with the slide-and o erable in one position to permit said rocking movement without transmission ofany motion-to the slide and operable other positio'n's'to cause varying amounts or motion to be transmitted to the slide during the; rocking m'evementof the-lever.

6; his machine for generating tapered gears, a=-f mfepa-work support, atool support, a cradle tea-1 tably mounted onthe frame and on which oire' ofsaid supportsisniounted, a slide mounted ontl'fei frame for movement in the direction of theflaxis of the cradle and on which the other supportis mounted, a work spindle journaled in the work support, a face mill gear cutter journaled in the tool support; means'for rotating the ciit'tei means for rotating the cradle and work spin-die in timed relation to effect generation of the tooth profiles, a pivoted lever operatively conrecreate the slide; means for rocking the lever about its pivot to im art movement to the slide during generation, and means for moving the leverbodil'y to move the slide toward or from the cradle toniove the work into or out of engagemerit w'rth the cutter.

7; n a machine for producing tapered gears, a trainee work support, a tool support, a cradle ojscillatab'ly mcu'r tea cn the frame and on which one f'said supports is mounted, a slide mounted I, f p "e for movement in the direction of the" axis of thecraale and which the other support is mounted, a work spindle journaleo in tfiejwcrk upport, a face nun "gear cutter journaieo' n the tool support, means for rotating the cuttenni ans for rotating the cradle and ere spindle in timed relation to generate the teeth profiles, a pivoted lever, means driven in time with the generating motion for rocking said leverabout its pivot througha given angle, ad justable means for connecting the lever with the slide 'a'nd operable in one position of its adjustmerit to permit said rocking, movement of the 1e' e'r without transmission of any motion to the slide and operable in other positions of its adju'stinent to cause varying amounts of'movement to be transmitted to the slide durin oscillating movement of the lever, and means for making the lever about aseparate pivot to move the work into and out of engagement with the cutter.

8. In a machine for producing tapered gears, a frame, a work support, a tool support, a cradle oscillatably mounted on the frame and on which one of said supports is'mounted, a slide mounted on the frame for movement in the direction of the axis bf the cradle edition which the other naled inthe tool support, means for'rotatingxthez cutter; means for rotating the cradle and'work.

I spindle in. timed relation to generate the tooth.-

profiles, a rotary cam, means for drivingisaid cam in timewith the generating motion, a lever-pivotedon the frame and operatively connected. to

said cam' to'rock on rotation of the cam, a second lever pivotally mounted on the first lever and operatively connected to the slide to impart.

movement to the slide on oscillation of the first lever about its pivot, and separate means for rocking the second lever about its pivotito impart:

added motion to the slide.

9. In a machine for producing tapered gears, a frame, a work support, a tool support, a cradle oscillatably mounted on the frame and on which one of said supports is mounted; a slide mounted on the frame for movement in the direction of the axis of the cradle and on which the other.- support' is mounted, a work spindle journaled on the work support, a face mill gear cutter journaled in the tool support, means for rotating the cutter, means for rotating the cradle and work spindle in timed relation to generate the tooth profiles, a rotary cam, means for driving said cam in time with the generating motion, a lever pivotedon the frame and operatively connected to said cam to rock on rotation of the cam, a sec- 0nd lever pivotally mounted on the first lever, a second cam driven in time withthe genera-ting motion and operatively connected to said second lever to rock said second lever on its pivot on rotation of said second cam, means operatively connecting the second lever to the slide toimpart movement to the slide on oscillation of the first lever about its pivot, said means being adjustable to permit the movement ofthe second lever to be transmitted to the slide also to impart additional movement to the slide.

10. Ih'a' machine for producing gears, a frame, a work support, a tool support, a slide reciprocably mounted on the frame and on whichone of said supports is mounted, a rotary cam, a lever pivotally mounted on the frame and operatively connecte'dboth to the slide and to the cam to effect reciprocation of the slide on rotation of the cam to effect relative movement between the tool and the work and through a limited path to move them relatively into and out of operative engagement, and means for moving the cam axially to effect relative movement between the tool and the work beyond said limited path to move the support, which is carried by the slide, from operative to loading positionand vice versa.

11. In a machine for producing tapered gears, a frame, a work support, a tool support, a cradle oscillatably mounted on the frame and on which one of said supports is mounted, a slide mounted on-the frame formovement in the direction of the axis of the cradle and on which the other support is mounted, a work spindle 'journa'l'ed m the work support, a face mill gear cutter journaled-in the tool support, means for rotating the cutter, means for rotating the cradleand work spindle in timedrelation to generate the tooth profiles, a rotary control member having a peripheral cam path and a peripheral groove formed therein, a'cam secured to the rotary control member to move therewith, a 'shaf-tt'o which the control member is fixed for rotation but on which the control member is axially slidable, a lever pivoted on the frame, a follower secured to-said lever and engaging in said cam path, a

second lever pivotally mounted on the first lever, means operatively connecting the second lever to the slide, a follower carried by the second lever and engaging said cam, said cam path being formed to move the slide toward and from the cradle to move the work into and out of engagement with the tool, said ca-m being formed to impart movement to the slide during generation, and a third lever pivoted on the frame and having a roller thereon engaging in a peripheral groove of the control member, said third lever being operable to move the control member axially to move the work to and from loading position.

12. In a machine for producing gears, a frame, a work support, a tool support, a cradle oscillatably mounted on the frame and on which one of said supports is mounted, a slide mounted on the frame for movement in the direction of the axis of the cradle and on which the other support is mounted, a work spindle journaled in the work support, a face mill gear cutter journaled in the tool support, means for rotating the cutter, means for rotating the cradle and the work spindle in timed relation to generate the tooth profiles, a member mounted on the slide and having a guide surface formed thereon, said member being adjustable to position said guide surface at any desired angle to the path of movement of the slide, means movable on the guide surface and operative to impart movement to the slide, the amount of said movement depending upon the angular position of the guide surface, a stop lug carried by said adjustable member, and a stop mounted on the frame and adapted to be engaged by the lug in the zero position of adjustment of said member to limit the movement of the slide toward the cradle to control the depth of the tooth spaces to be cut into the work.

13. In a machine for producing gears, a frame, a work support, a tool support, a cradle oscillatably mounted on the frame and on which one of said supports is mounted, a slide mounted on the 14 frame for movement in the direction of the axis of the cradleand on which the other support is mounted, a work spindle journaled in the work support, a face mill gear cutter journaled in the tool support, means for rotating the cutter, means for rotating the cradle and work spindle in timed relation to generate the tooth profiles, a block adjustable on the slide in the direction of the axis of the cradle, a plate having a guide surface formed thereon, said plate being adjustable angularly on the block to position the guide surface at any desired angle to the direction of movement of the slide, a member movable in a plane at right angles to the direction of movement of the slide and engaging said guide surface to impart movement to the slide when the guide surface is inclined at other than right angles to the path of movement of the slide, separate means for moving the slide to and from operative position, a stop on the frame, and a stop lug mounted on the plate and adapted to engage said stop when the plate is in the zero position of its adjustment to limit inward movement of the slide toward the cradle under actuation of the last named means.

OLIVER F. BAUER.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS 

